[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

US7870785B2 - Positive displacement flowmeter - Google Patents

Positive displacement flowmeter Download PDF

Info

Publication number
US7870785B2
US7870785B2 US12/735,276 US73527608A US7870785B2 US 7870785 B2 US7870785 B2 US 7870785B2 US 73527608 A US73527608 A US 73527608A US 7870785 B2 US7870785 B2 US 7870785B2
Authority
US
United States
Prior art keywords
pair
positive displacement
displacement flowmeter
curve
rotor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US12/735,276
Other versions
US20100281970A1 (en
Inventor
Seigo Ono
Katsuichi Uchida
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Oval Corp
Original Assignee
Oval Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Oval Corp filed Critical Oval Corp
Assigned to OVAL CORPORATION reassignment OVAL CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ONO, SEIGO, UCHIDA, KATSUICHI
Publication of US20100281970A1 publication Critical patent/US20100281970A1/en
Application granted granted Critical
Publication of US7870785B2 publication Critical patent/US7870785B2/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F3/00—Measuring the volume flow of fluids or fluent solid material wherein the fluid passes through the meter in successive and more or less isolated quantities, the meter being driven by the flow
    • G01F3/02—Measuring the volume flow of fluids or fluent solid material wherein the fluid passes through the meter in successive and more or less isolated quantities, the meter being driven by the flow with measuring chambers which expand or contract during measurement
    • G01F3/04—Measuring the volume flow of fluids or fluent solid material wherein the fluid passes through the meter in successive and more or less isolated quantities, the meter being driven by the flow with measuring chambers which expand or contract during measurement having rigid movable walls
    • G01F3/06—Measuring the volume flow of fluids or fluent solid material wherein the fluid passes through the meter in successive and more or less isolated quantities, the meter being driven by the flow with measuring chambers which expand or contract during measurement having rigid movable walls comprising members rotating in a fluid-tight or substantially fluid-tight manner in a housing
    • G01F3/10—Geared or lobed impeller meters

Definitions

  • the present invention relates to a positive displacement flowmeter and, more particularly, to a positive displacement flowmeter using a pitch curve itself of non-circular gears as a rotor tooth profile.
  • a locus of a contact point of external gear tooth profiles making continuous contact generally forms a lemniscate loop curve and if this loop is flattened toward a center line between axes and coincides with the center line, the contact point moves on the center of both gears. Therefore, the tooth profile has a contour that achieves rolling motion, which corresponds to a pitch curve of non-uniform speed gear (non-circular gear).
  • a contour of a rolling contact wheel which has a constant center distance and an angular velocity ratio that varies during rotation is a non-circular curve and a non-circular gear is a gear provided with teeth using this non-circular curve as a pitch curve to ensure transmission.
  • a transmissible tooth profile is generally provided on the pitch curve. This tooth profile may be involute, cycloidal/trochoidal, Novikov, or a combination thereof, each of which has drawback and advantage.
  • a helical gear positive displacement flowmeter described in Patent Document 1 uses a single-point continuous contact tooth profile of a single curve.
  • the single-point continuous contact tooth profile is ideal for a rotor tooth profile of a flowmeter since higher surface pressure bearing strength is expected due to convex/concave contact of tooth surfaces and no trapping phenomenon occurs which is disadvantageous to a flowmeter.
  • the single-point continuous contact tooth profile represented by a sine-curve gear has a helical shape due to a contact ratio and the tooth height ratio is limited to 0.785 m, i.e., nm/4 (m: module) if formed by a single curve. This is disadvantageous to a rotor of a flowmeter in aspect of function or production.
  • a pitch curve of a non-circular gear is considered as an ideal tooth profile curve that enables the continuous contact and the rolling contact instead of slide contact between tooth profiles as a gear tooth profile. It is assumed that a tooth profile of a flowmeter rotor is formed by a pitch curve (rolling-contact curve) of an oval gear that is a type of non-circular gears. In this case, it is known that the tooth profile does not act as a gear since a tooth profile for certainly transmitting the rotation is not included.
  • Patent Document 1 Japanese Patent Publication No. 3310239
  • the present invention was conceived in view of the above situations and it is therefore the object of the present invention to provide a positive displacement flowmeter having a pair of non-circular gears making rolling contact without slip on a pitch line.
  • a second technical means is the first technical means wherein the pair of the non-circular gears has a spur shape.
  • a third technical means is the first or second technical means wherein when the pair of the non-circular gears is in an engaged state at an equivalent radius position, a gap is provided between tooth shapes on long radius side of one of the non-circular gears and short radius side of the other non-circular gear.
  • a fourth technical means is any one of the first or second technical means wherein the pair of the non-circular gears is made up of the same shaped non-circular gears.
  • abrasion resistance is achieved since a pair of non-circular gears of a positive displacement flowmeter makes rolling contact without slip on a pitch line; a higher torque efficiency is achieved since a larger value can be given to a tooth height ratio; and it is possible to form the gears in spur shape instead of helical shape while avoiding abnormal engagement since apparent backlash is provided.
  • FIG. 1 is a diagram of an exemplary configuration of a positive displacement flowmeter according to one embodiment of the present invention.
  • FIG. 1 is a diagram of an exemplary configuration of a positive displacement flowmeter according to one embodiment of the present invention.
  • FIGS. 1 , 1 and 2 denote a pair of rotors; 3 denotes a casing; 4 an 5 denote axial centers of the rotors 1 and 2 , respectively; 6 denotes a virtual pitch circle of the rotor 1 ; 7 denotes a virtual pitch circle of the rotor 2 ; 8 denotes an addendum circle of the rotor 1 ; and 9 denotes an addendum circle of the rotor 2 .
  • a pair of the rotors 1 , 2 is housed in the casing 3 of the positive displacement flowmeter rotatably around the axial centers 4 , 5 .
  • the moving radius is represented by the following Eq. (1) for the oval pitch curve that is a rolling contact curve (closed curve), where a, b, n and ⁇ i denote a homothetic coefficient, a flattening, a number of lobes, and a moving angle, respectively.
  • r L a/( 1 ⁇ b ) Eq. (2)
  • r S a/( 1 +b ) Eq. (3)
  • the second interference is interference generated by substantial portions of tooth shapes with each other at an irrelevant position other than the contact point P in the course of movement of the contact point P along a given locus.
  • K i.e., a distance between the axial centers 4 and 5
  • the flattening b is set to 0.5
  • the homothetic coefficient a is obtained as 3.75 from the following Eq. (4).
  • a K (1 ⁇ b 2 )/2 Eq. (4)
  • the torque is greater in the right rotor 2 than the left rotor 1 in the state of FIG. 1 and, therefore, the right rotor 2 acts as the driving side to rotate the left rotor 1 in the direction of arrows in FIG. 1 .
  • FIG. 2(B) is an enlarged diagram of an X portion of FIG. 2(A) .
  • the transition of the engagement state is depicted when the rotors 1 , 2 rotate from 0° to 30° in the order of FIG. 3(A) to FIG. 3(F) .
  • P denotes the contact point of the rotors 1 , 2
  • t denotes the apparent backlash between the rotors 1 , 2 .
  • the rotors 1 and 2 are housed in the casing 3 rotatably around the axial centers 4 and 5 , the casing 3 is not illustrated.
  • FIG. 3(A) shows the case when the angle ⁇ 1 of the rotor 1 is 0° and the angle ⁇ 2 of the rotor 2 is 0°
  • FIG. 3(B) shows the case when the angle ⁇ 1 of the rotor 1 is 10.00° and the angle ⁇ 2 of the rotor 2 is 20.00°
  • FIG. 3(C) shows the case when the angle ⁇ 1 of the rotor 1 is 15.00° and the angle ⁇ 2 of the rotor 2 is 23.86°.
  • FIG. 3(D) shows the case when the angle ⁇ 1 of the rotor 1 is 18.00° and the angle ⁇ 2 of the rotor 2 is 25.46°;
  • FIG. 3(E) shows the case when the angle ⁇ 1 of the rotor 1 is 24.00° and the angle ⁇ 2 of the rotor 2 is 27.94°;
  • FIG. 3(F) shows the case when the angle ⁇ 1 of the rotor 1 is 30.00° and the angle ⁇ 2 of the rotor 2 is 30.00°.
  • the apparent backlash t is minimized and the measured value thereof is about 0.07 mm.
  • the present invention may be implemented by appropriately setting the flattening b even when the number of lobes n is 8.
  • the flattening b is set to 0.34.
  • the measured value of the apparent backlash t in this case is about 0.02 mm (minimum value).
  • the transition of the engagement state is depicted when the rotors 1 , 2 rotate from 0° to 22.5° in the order of FIG. 4(A) to FIG. 4(F) .
  • P denotes the contact point of the rotors 1 , 2
  • t denotes the apparent backlash between the rotors 1 , 2 .
  • the rotors 1 and 2 are housed in the casing 3 rotatably around the axial centers 4 and 5 , the casing 3 is not illustrated.
  • FIG. 4(A) shows the case when the angle ⁇ 1 of the rotor 1 is 0° and the angle ⁇ 2 of the rotor 2 is 0°
  • FIG. 4(B) shows the case when the angle ⁇ 1 of the rotor 1 is 10.53° and the angle ⁇ 2 of the rotor 2 is 6.00°
  • FIG. 4(C) shows the case when the angle ⁇ 1 of the rotor 1 is 13.97° and the angle ⁇ 2 of the rotor 2 is 9.00°.
  • FIG. 4(D) shows the case when the angle ⁇ 1 of the rotor 1 is 18.53° and the angle ⁇ 2 of the rotor 2 is 15.00°
  • FIG. 4(E) shows the case when the angle ⁇ 1 of the rotor 1 is 20.23° and the angle ⁇ 2 of the rotor 2 is 18.00°
  • FIG. 4(F) shows the case when the angle ⁇ 1 of the rotor 1 is 22.50° and the angle ⁇ 2 of the rotor 2 is 22.50°.
  • the apparent backlash t is minimized and the measured value thereof is about 0.02 mm.

Landscapes

  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Measuring Volume Flow (AREA)
  • Rotary Pumps (AREA)

Abstract

A position displacement flowmeter having a pair of non-circular gears in a rolling contact on a pitch line without slippage. The positive displacement flowmeter comprises a casing and a pair of rotors provided in the casing and rotatable around its center axes. The pair of rotors, have a tooth profile curve which is an oval pitch curve itself having a trajectory of contact points on the pitch line, and they satisfy a condition of r1+r2=K=const r1 dθ1=r2 dθ2, and a moving radius of the oval pitch curve is given by ri=a/(1−b cos nθi) (i=1, 2), where “ri (i=1, 2)” is the moving radius that is a distance from a center of rotation to the oval pitch curve, “a” is a homothetic coefficient, “b” is a flattening, “n” is a number of lobes, and “θi (i=1, 2) is a moving angle.

Description

TECHNICAL FIELD
The present invention relates to a positive displacement flowmeter and, more particularly, to a positive displacement flowmeter using a pitch curve itself of non-circular gears as a rotor tooth profile.
BACKGROUND OF THE INVENTION
A locus of a contact point of external gear tooth profiles making continuous contact generally forms a lemniscate loop curve and if this loop is flattened toward a center line between axes and coincides with the center line, the contact point moves on the center of both gears. Therefore, the tooth profile has a contour that achieves rolling motion, which corresponds to a pitch curve of non-uniform speed gear (non-circular gear).
A contour of a rolling contact wheel which has a constant center distance and an angular velocity ratio that varies during rotation is a non-circular curve and a non-circular gear is a gear provided with teeth using this non-circular curve as a pitch curve to ensure transmission. A transmissible tooth profile is generally provided on the pitch curve. This tooth profile may be involute, cycloidal/trochoidal, Novikov, or a combination thereof, each of which has drawback and advantage.
For example, a helical gear positive displacement flowmeter described in Patent Document 1 uses a single-point continuous contact tooth profile of a single curve. The single-point continuous contact tooth profile is ideal for a rotor tooth profile of a flowmeter since higher surface pressure bearing strength is expected due to convex/concave contact of tooth surfaces and no trapping phenomenon occurs which is disadvantageous to a flowmeter. However, the single-point continuous contact tooth profile represented by a sine-curve gear has a helical shape due to a contact ratio and the tooth height ratio is limited to 0.785 m, i.e., nm/4 (m: module) if formed by a single curve. This is disadvantageous to a rotor of a flowmeter in aspect of function or production.
On the other hand, a pitch curve of a non-circular gear is considered as an ideal tooth profile curve that enables the continuous contact and the rolling contact instead of slide contact between tooth profiles as a gear tooth profile. It is assumed that a tooth profile of a flowmeter rotor is formed by a pitch curve (rolling-contact curve) of an oval gear that is a type of non-circular gears. In this case, it is known that the tooth profile does not act as a gear since a tooth profile for certainly transmitting the rotation is not included.
Patent Document 1: Japanese Patent Publication No. 3310239
However, in the case of rotors of a positive displacement flowmeter housed as a pair in a measuring chamber of the flowmeter to transmit rotation through energy of fluid, although the torque transmission is switched at a position of the equal diameters where the torques are theoretically equalized and a tooth surface on the opposite side comes into contact, if an appropriate gap considered as an apparent backlash may be formed, abnormal engagements may be reduced and the tooth profiles making the rolling contact may be realized. However, in a conventional positive displacement flowmeter, the technical idea as described above for using the tooth profile with the rolling-contact curve as the rotor does not exist and has not been realized.
The present invention was conceived in view of the above situations and it is therefore the object of the present invention to provide a positive displacement flowmeter having a pair of non-circular gears making rolling contact without slip on a pitch line.
SUMMARY OF THE INVENTION
To solve the problem, a first technical means of the present invention is a positive displacement flowmeter provided with a pair of non-circular gears in a casing, wherein the pair of the non-circular gears has an oval pitch curve itself having a locus of a contact point on a pitch line as a tooth profile curve and satisfies conditions of
r 1 +r 2 =K=const., and
r 1 ·dθ 1 =r 2 ·dθ 2,
and a moving radius of the oval pitch curve is represented by ri=a/(1−b cos nθi) (i=1, 2)
(where ri (i=1, 2) denotes a moving radius that is a distance from the rotation center to the oval pitch curve, and a, b, n and θi (i=1, 2) denote similarity coefficient, flattening, number of lobes, and moving angle, respectively).
A second technical means is the first technical means wherein the pair of the non-circular gears has a spur shape.
A third technical means is the first or second technical means wherein when the pair of the non-circular gears is in an engaged state at an equivalent radius position, a gap is provided between tooth shapes on long radius side of one of the non-circular gears and short radius side of the other non-circular gear.
A fourth technical means is any one of the first or second technical means wherein the pair of the non-circular gears is made up of the same shaped non-circular gears.
A fifth technical means is any one of the first to fourth technical means wherein the number of lobes n and the flattening b are set to 6 and 0.5, respectively, in the equation ri=a/(1−b cos nθi) (i=1, 2) representing the moving radius of the oval pitch curve.
A sixth technical means is any one of the first or second technical means wherein the number of lobes n and the flattening b are set to 8 and 0.34, respectively, in the equation ri=a/(1−b cos nθi) (i=1, 2) representing the moving radius of the oval pitch curve.
According to the present invention, excellent abrasion resistance is achieved since a pair of non-circular gears of a positive displacement flowmeter makes rolling contact without slip on a pitch line; a higher torque efficiency is achieved since a larger value can be given to a tooth height ratio; and it is possible to form the gears in spur shape instead of helical shape while avoiding abnormal engagement since apparent backlash is provided.
BRIEF DESCRIPTION OF DRAWINGS
FIG. 1 is a diagram of an exemplary configuration of a positive displacement flowmeter according to one embodiment of the present invention.
FIG. 2 is a diagram of an example of an engagement state at an equivalent radius position in the case of the number of lobes n=6.
FIG. 3 is a diagram of a transition example of an engagement state of a pair of rotors in the case of the number of lobes n=6.
FIG. 4 is a diagram of a transition example of an engagement state of a pair of rotors in the case of the number of lobes n=8.
 EXPLANATIONS OF LETTERS OR NUMERALS
1, 2 . . . rotor; 3 . . . casing; 4, 5 . . . axial center; 6, 7 . . . virtual pitch circle; and 8, 9 . . . addendum circle
DESCRIPTION OF PREFERRED EMBODIMENTS
Preferred embodiments of a positive displacement flowmeter of the present invention will now be described with reference to the accompanying drawings.
FIG. 1 is a diagram of an exemplary configuration of a positive displacement flowmeter according to one embodiment of the present invention. In FIGS. 1, 1 and 2 denote a pair of rotors; 3 denotes a casing; 4 an 5 denote axial centers of the rotors 1 and 2, respectively; 6 denotes a virtual pitch circle of the rotor 1; 7 denotes a virtual pitch circle of the rotor 2; 8 denotes an addendum circle of the rotor 1; and 9 denotes an addendum circle of the rotor 2. A pair of the rotors 1, 2 is housed in the casing 3 of the positive displacement flowmeter rotatably around the axial centers 4, 5. The rotors 1, 2 are formed in spur shape and use a tooth profile curve that is an oval pitch curve itself having a locus of a contact point P on a pitch line that links the axial centers 4 and 5 and satisfy the following rolling contact condition:
r 1 +r 2 =K=const., and
r 1 ·dθ 1 =r 2 ·dθ 2
where r1, r2 denote moving radii that are distances from the rotation center to the oval pitch curve and θ1, θ2 denote moving angles.
The moving radius is represented by the following Eq. (1) for the oval pitch curve that is a rolling contact curve (closed curve), where a, b, n and θi denote a homothetic coefficient, a flattening, a number of lobes, and a moving angle, respectively.
r i =a/(1−b cos nθ i) (i=1, 2)  Eq. (1)
A long radius rL and a short radius rS are represented by the following Eq. (2) and Eq. (3).
r L =a/(1−b)  Eq. (2)
r S =a/(1+b)  Eq. (3)
Since a larger discharge amount per rotation is required in the case of the positive displacement flowmeter, it is desirable to reduce the number of teeth as much as possible and it is desirable to increase a long/short radius ratio (rL/rS) to increase the torque efficiency. However, since a fewer number of teeth problematically causes abnormal engagement due to second interference and a larger long/short radius ratio problematically causes the deterioration of strength of the gears, a balance must be achieved between the number of teeth and the long/short radius ratio. The second interference is interference generated by substantial portions of tooth shapes with each other at an irrelevant position other than the contact point P in the course of movement of the contact point P along a given locus.
In the following examples, the number of lobes n is an even number and results of simulations will be described with a representative example of n=6. When a center distance K, i.e., a distance between the axial centers 4 and 5 is set to 10 mm and the flattening b is set to 0.5, the homothetic coefficient a is obtained as 3.75 from the following Eq. (4). In this case, the long/short radius ratio is rL/rS=3.0.
a=K(1−b 2)/2  Eq. (4)
A simulation result will be described for the case of the center distance K=10 mm and the parameters of Eq. (1), the number of lobes n=6, the flattening b=0.5, and the homothetic coefficient a=3.75 with reference to FIGS. 1 and 2. In the case of this example, it is assumed that the rotors 1, 2 are made up of the same shaped non-circular gears.
FIG. 1 exemplarily illustrates a state of engagement at a long/short radius position in the case of the number of lobes n=6. In this case, if a pair of the rotors 1, 2 is disposed within fluid F, rotation torques are generated in both of the rotors 1, 2. In general, the engagement (contact) generates more torques from the short radius rs to the long radius rL and the switching point is at the equivalent radius position depicted in FIG. 2(A), i.e., a position having equivalent radii (r1=r2) where the torques are equivalent to each other. Therefore, if the fluid F flows in the direction of an arrow (upwardly), the torque is greater in the right rotor 2 than the left rotor 1 in the state of FIG. 1 and, therefore, the right rotor 2 acts as the driving side to rotate the left rotor 1 in the direction of arrows in FIG. 1.
FIG. 2(A) is a diagram of an example of the engagement state at the equivalent radius position in the case of the number of lobes n=6. FIG. 2(B) is an enlarged diagram of an X portion of FIG. 2(A).
As depicted in FIG. 2(A), when the engagement (contact) of the rotors 1, 2 comes to the equivalent radius position (r1=r2), the torques of the rotors 1, 2 become equivalent and the left rotor 1 is instantaneously switched to the driving side from this state. Like this, in the case of the number of lobes n=6, it is known that the second interference does not occur on the substantial side in either the contact state at the long/short radius position (r1·r2) depicted in FIG. 1 or the contact state at the equivalent radius position (r1=r2) depicted in FIG. 2.
As shown in FIG. 2(B), when a pair of the rotors 1, 2 is in the engagement state at the equivalent radius position (r1=r2), a gap is provided between the long radius side of the rotor 2 and the short radius side of the rotor 1. This gap is referred to an apparent backlash (hereinafter, apparent backlash t). The apparent backlash t is about 0.12 mm when measured in the engagement state at the equivalent radius position. The center distance K in this case is 10 mm.
As above, excellent abrasion resistance is achieved since a pair of non-circular gears of a positive displacement flowmeter makes rolling contact without slip on a pitch line; a higher torque efficiency is achieved since a larger value is given to a tooth height ratio; and it is possible to from the gears in spur shape instead of helical shape while avoiding abnormal engagement since the apparent backlash is provided.
FIG. 3 is a diagram of a transition example of the engagement state of a pair of the rotors 1, 2 in the case of the number of lobes n=6. The transition of the engagement state is depicted when the rotors 1, 2 rotate from 0° to 30° in the order of FIG. 3(A) to FIG. 3(F). In FIG. 3, P denotes the contact point of the rotors 1, 2 and t denotes the apparent backlash between the rotors 1, 2. Although the rotors 1 and 2 are housed in the casing 3 rotatably around the axial centers 4 and 5, the casing 3 is not illustrated.
FIG. 3(A) shows the case when the angle θ1 of the rotor 1 is 0° and the angle θ2 of the rotor 2 is 0°; FIG. 3(B) shows the case when the angle θ1 of the rotor 1 is 10.00° and the angle θ2 of the rotor 2 is 20.00°; and FIG. 3(C) shows the case when the angle θ1 of the rotor 1 is 15.00° and the angle θ2 of the rotor 2 is 23.86°.
FIG. 3(D) shows the case when the angle θ1 of the rotor 1 is 18.00° and the angle θ2 of the rotor 2 is 25.46°; FIG. 3(E) shows the case when the angle θ1 of the rotor 1 is 24.00° and the angle θ2 of the rotor 2 is 27.94°; and FIG. 3(F) shows the case when the angle θ1 of the rotor 1 is 30.00° and the angle θ2 of the rotor 2 is 30.00°. In FIG. 3(D), the apparent backlash t is minimized and the measured value thereof is about 0.07 mm.
Although the embodiment has been described as a representative example when the number of lobes n is 6, the present invention may be implemented by appropriately setting the flattening b even when the number of lobes n is 8. For example, in the case of the number of lobes n=8, the flattening b is set to 0.34. The measured value of the apparent backlash t in this case is about 0.02 mm (minimum value).
FIG. 4 is a diagram of a transition example of the engagement state of a pair of the rotors 1, 2 in the case of the number of lobes n=8. The transition of the engagement state is depicted when the rotors 1, 2 rotate from 0° to 22.5° in the order of FIG. 4(A) to FIG. 4(F). In FIG. 4, P denotes the contact point of the rotors 1, 2 and t denotes the apparent backlash between the rotors 1, 2. Although the rotors 1 and 2 are housed in the casing 3 rotatably around the axial centers 4 and 5, the casing 3 is not illustrated.
FIG. 4(A) shows the case when the angle θ1 of the rotor 1 is 0° and the angle θ2 of the rotor 2 is 0°; FIG. 4(B) shows the case when the angle θ1 of the rotor 1 is 10.53° and the angle θ2 of the rotor 2 is 6.00°; and FIG. 4(C) shows the case when the angle θ1 of the rotor 1 is 13.97° and the angle θ2 of the rotor 2 is 9.00°.
FIG. 4(D) shows the case when the angle θ1 of the rotor 1 is 18.53° and the angle θ2 of the rotor 2 is 15.00°; FIG. 4(E) shows the case when the angle θ1 of the rotor 1 is 20.23° and the angle θ2 of the rotor 2 is 18.00°; and FIG. 4(F) shows the case when the angle θ1 of the rotor 1 is 22.50° and the angle θ2 of the rotor 2 is 22.50°. In FIG. 4(D), the apparent backlash t is minimized and the measured value thereof is about 0.02 mm.

Claims (6)

1. A positive displacement flowmeter provided with a pair of non-circular gears in a casing, wherein
the pair of the non-circular gears has an oval pitch curve itself having a locus of a contact point on a pitch line as a tooth profile curve and satisfies conditions of

r 11+r 2 =K=const., and

r 1 ·dθ 1 =r 2 ·dθ 2,
and a moving radius of the oval pitch curve is represented by r1=a/(1−b cos nθ1) (i=1, 2)
(where ri (i=1, 2) denotes a moving radius that is a distance from the rotation center to the oval pitch curve, and a, b, n and θi (i=1, 2) denote similarity coefficient, flattening, number of lobes, and moving angle, respectively).
2. The positive displacement flowmeter as defined in claim 1, wherein the pair of the non-circular gears has a spur shape.
3. The positive displacement flowmeter as defined in claim 1 or 2, wherein when the pair of the non-circular gears is in an engaged state at an equivalent radius position, a gap is provided between tooth shapes on long radius side of one of the non-circular gears and short radius side of the other non-circular gear.
4. The positive displacement flowmeter as defined in claim 1 or 2, wherein the pair of the non-circular gears is made up of the same shaped non-circular gears.
5. The position displacement flowmeter as defined in claim 1 or 2, wherein the number of lobes n and the flattening b are set to 6 and 0.5, respectively, in the equation ri=a/(1−bs cos nθi) (i=1, 2) representing the moving radius of the oval pitch curve.
6. The positive displacement flowmeter as defined in claim 1 or 2, wherein the number of lobes n and the flattening b are set to 8 and 0.34, respectively, in the equation ri=a/(1−bs cos nθi) (i=1, 2) representing the moving radius of the oval pitch curve.
US12/735,276 2008-01-24 2008-03-06 Positive displacement flowmeter Expired - Fee Related US7870785B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2008-013529 2008-01-24
JP2008013529A JP4203531B1 (en) 2008-01-24 2008-01-24 Volumetric flow meter
PCT/JP2008/054019 WO2009093342A1 (en) 2008-01-24 2008-03-06 Positive displacement flowmeter

Publications (2)

Publication Number Publication Date
US20100281970A1 US20100281970A1 (en) 2010-11-11
US7870785B2 true US7870785B2 (en) 2011-01-18

Family

ID=40325644

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/735,276 Expired - Fee Related US7870785B2 (en) 2008-01-24 2008-03-06 Positive displacement flowmeter

Country Status (7)

Country Link
US (1) US7870785B2 (en)
EP (1) EP2241865A1 (en)
JP (1) JP4203531B1 (en)
KR (1) KR101190388B1 (en)
CN (1) CN101925803B (en)
TW (1) TW200933126A (en)
WO (1) WO2009093342A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4599454B1 (en) * 2009-09-07 2010-12-15 株式会社オーバル Volumetric gas-liquid two-phase flow meter and multi-phase flow measurement system
KR102160400B1 (en) 2019-05-28 2020-10-05 한국생산기술연구원 Positive displacement turbine for pressure pulsation reduction

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5769211A (en) 1980-10-17 1982-04-27 Akitoshi Kitano Flowmeter for suspension
JPS60166775A (en) 1984-02-09 1985-08-30 Kinmon Seisakusho:Kk Noncircular gear
JPS63191923A (en) 1987-02-04 1988-08-09 Aichi Tokei Denki Co Ltd Manufacture of rotator for flowmeter
US5050094A (en) * 1988-01-26 1991-09-17 Akitoshi Kitano Compensating method and device for instrumental error in rotary displacement flowmeter
JP2000346689A (en) 1999-06-09 2000-12-15 Oval Corp Improvement of noncircular gear and noncircular gear- type flowmeter using it
JP2001027560A (en) 1999-07-14 2001-01-30 Oval Corp Helical gear type capacity flowmeter

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5769211A (en) 1980-10-17 1982-04-27 Akitoshi Kitano Flowmeter for suspension
JPS60166775A (en) 1984-02-09 1985-08-30 Kinmon Seisakusho:Kk Noncircular gear
JPS63191923A (en) 1987-02-04 1988-08-09 Aichi Tokei Denki Co Ltd Manufacture of rotator for flowmeter
US5050094A (en) * 1988-01-26 1991-09-17 Akitoshi Kitano Compensating method and device for instrumental error in rotary displacement flowmeter
JP2000346689A (en) 1999-06-09 2000-12-15 Oval Corp Improvement of noncircular gear and noncircular gear- type flowmeter using it
JP2001027560A (en) 1999-07-14 2001-01-30 Oval Corp Helical gear type capacity flowmeter
JP3310239B2 (en) 1999-07-14 2002-08-05 株式会社オーバル Helical gear type positive displacement flowmeter

Also Published As

Publication number Publication date
TWI354095B (en) 2011-12-11
JP4203531B1 (en) 2009-01-07
EP2241865A1 (en) 2010-10-20
KR20100101704A (en) 2010-09-17
WO2009093342A1 (en) 2009-07-30
CN101925803B (en) 2012-07-04
US20100281970A1 (en) 2010-11-11
CN101925803A (en) 2010-12-22
KR101190388B1 (en) 2012-10-11
TW200933126A (en) 2009-08-01
JP2009174986A (en) 2009-08-06

Similar Documents

Publication Publication Date Title
CN101109436B (en) Speed increasing or speed reducing gear pair adapted for power transmission
US8070640B2 (en) Fluctuating gear ratio limited slip differential
US20050059524A1 (en) Internal planetary gear mechanism
US9903459B2 (en) Strain wave gearing having continuous-contact tooth profile formed using arcuate tooth profile
TWI614428B (en) Dual type strain wave gearing
US8425212B2 (en) Positive displacement flowmeter and helical gear
EP3348869A1 (en) Conjugate curve-based cylindrical gear meshing pair having multiple contact points
TWI620883B (en) Dual type strain wave gearing
CN106352025A (en) Harmonic speed reducer
EP3306132B1 (en) Strain wave gearing device with compound meshing that involves congruity of tooth surfaces
WO2016013383A1 (en) Dual-type wave gear device
CN114198464A (en) Gear pair and nutation speed reducer
CN202690900U (en) Novel tooth-shaped gear eccentric drive mechanism
US7870785B2 (en) Positive displacement flowmeter
US10174825B2 (en) Passing-type-meshing negative-deflection strain wave gearing
CN111219447B (en) Cambered surface secondary envelope crown gear nutation transmission device
WO2024207693A1 (en) Parabolic tooth trace gear mechanism having circular arc and parabola combined end face tooth profile
CN111637193A (en) Inner gearing helical gear transmission mechanism
US20100317483A1 (en) High performance differential
CN113280081A (en) Non-sliding parallel axis gear mechanism with separable center distance
JPS61153040A (en) Speed reduction gear
WO2005056367A1 (en) Electric power steering device
CN113483075A (en) Design method of inner tooth profile of cycloid outer ring, cycloid outer ring and cycloid speed reducer
RU2390670C1 (en) Cycloid gear
CN109241679A (en) Etc. relative curvatures gear and its design method

Legal Events

Date Code Title Description
AS Assignment

Owner name: OVAL CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:ONO, SEIGO;UCHIDA, KATSUICHI;REEL/FRAME:025240/0455

Effective date: 20100420

REMI Maintenance fee reminder mailed
LAPS Lapse for failure to pay maintenance fees
STCH Information on status: patent discontinuation

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362

FP Lapsed due to failure to pay maintenance fee

Effective date: 20150118